Telegraph apparatus (5-unit-code) for the setting of symbols which are arranged on a type cylinder



May 5, 1970 H. KERN 3,510,583

TELEGRAPH APPARATUS FOR THE SETTING 5-UNIT-CODE) 0 YMBOLS WHICH AREARRANGED 0N Filed Jan. 25, 1.

A TYPE CYLINDER 4 Sheets-Sheet 1 May 5, 1970 H. KERN 3,510,583

TELEGRAPH APPARATUS (B-UNIT-CODE) FOR THE SETTING 0F SYMBOLS WHICH AREARRANGED ON A TYPE CYLINDER Filed Jan. 25. 1.967 4 Sheets-Sheet 2 Fig.2

May 5, 1970 H. KERN 3,510,583

1 TELEGRAPH A RATUS (S-UNIT-CODE) FOR THE SETTING SYMBOLS CH AREARRANGED ON A TYPE CYLINDER Filed Jan. 25. 7 4 Sheets-Sheet 5 H. KERN3,510583 UNIT -CO FOR THE SETTING DER May 5, 1970 TELEGRAPH APPARATUS(5' DE) E ARRANGED ON A TYPE CYLIN 4 She OF SYMBOLS WHICH AR 1.967

ets-Sheet 4.

Filed Jan. 23;

United States Patent TELEGRAPH APPARATUS (S-UNIT-CODE) FOR THE SE'ITIN G0F SYMBOLS WHICH ARE AR- RANGED ON A TYPE CYLINDER Hans Kern, 14Schuckertstn,

8 Munich 25, Germany Filed Jan. 23, 1967, Ser. No. 610,902 Claimspriority, application Germany, Jan. 28, 1966, S 101,673, S 101,674, S101,675 Int. Cl. H041 17/24 US. Cl. 178-34 13 Claims ABSTRACT OF THEDISCLOSURE A telegraph apparatus (S-unit-code) for the setting ofsymbols which are arranged on the circumference of a type cylinder ineight symbol rows extending in an axial direction. The type cylinder isdriven by successively connected planetary gears (combined planetarygear mechanism) which are rendered operable by setting memberscontrolled by a binary code system. The combined planetary gearmechanism has a gear ratio of 1:2, or 2:1 per gear stage. Moreover, theinvention concerns a coupling system for the selective engagement ofcams 'for onehalf of a revolution. The cams provide an input to theindividual stages of the combined planetary gear mechanism for thesetting of a type-cylinder having a plurality of symbols in anelectrically operated typewriter.

CROSS-REFERENCES TO RELATED APPLICATIONS Applicant claims priority fromcorresponding German applications Ser. Nos. 101,673; 101,674 and101,675, filed on Jan. 28, 1966.

BACKGROUND OF THE INVENTION In the utilization of high speed typecylinder printers it is necessary to keep the mass to be moved to aminimum. Also, the apparatus for setting the type cylinder must bedeveloped in such a way that the movement necessary to set the typecylinder is as small as possible. It is also important to maximize thetime available for setting the type cylinder printer and minimize thetime necessary for actuating the same.

There is known in the prior art an arrangement for setting a typecylinder printer on which there is arranged on the circumference of thecylinder in an axial direction eight rows of symbols. In thisarrangement, for the axial and rotary setting of the type cylinder,there is provided a two-stage combined planetary gear mechanism having afirst sun gear and two planetary gear pairs which are selectivelyoperable by connecting rods associated therewith. As compared to otherknown developments, there are considerable advantages obtained throughsuch a system. For example, the combined two planetary gear mechanismcontrolled by the setting rods turn or slide the type cylinder directlyfrom one printing position into the next. In contrast to this, otherknown printers require that the type cylinder return to its initialposition prior to each new setting. Also, in this known combinedplanetary gear mechanism it is possible to operate with equal settingstrokes.

Accordingly, it is an object of the invention to provide an improvedcombined planetary gear mechanism for setting the type cylinder in sucha way that the mechanism is simplified and permits larger manufacturingtolerances while still insuring that the type cylinder is brought intoprecise printing position.

In the utilization of high speed type cylinder printers it is necessaryto move the type cylinder into the printing position as quickly aspossible. When a combined planetary gear mechanism is utilized forsetting the type cylinder, it is not possible to utilize the binary codesetting signals directly for shifting the type cylinder since the energylevel of the signal is too low. Therefore, it is desirable to employ anauxiliary drive for shifting the type cylinder, which is energized bythe setting signal.

Moreover, it is necessary in obtaining high speed operation that thetype cylinder not have to be returned to a rest position after eachprinting, as this results in a loss of time. It is preferred that thetype cylinder be moved directly from one position to the next without areturn to a rest position.

There is known in the prior art an apparatus which employs a two-stagecombined planetary gear mechanism for the axial and rotary setting ofthe type cylinder. The combined planetary gear mechanism includes afirst sun wheel and two planetary gear pairs which are selectivelyoperable by connecting rods associated therewith. In this arrangement,one of the two connecting rods, operating in an opposite sense from theother and selectable among the connecting rods, is positioned in thearea of an extension which can be turned around a fixed axis through acontrol cam in such a way that the first sun gear and the two planetarygear pairs of the combined planetary gear mechanism are operable by themovement of the extension. This arrangement guarantees a fast operationof the setting system with a low amount of power. The position of theindividual connecting rods and the individual stages of the two stagecombined planetary gear mechanism remain stationary until a difierentposition is required for the printing of the next symbol.

Another possibility exists for operating the individual stages of acombined planetary gear mechanism utilize-d for setting a type cylinder.In this case, the setting signal is communicated to the combinedplanetary gear mechanism by an auxiliary drive which utilizes eccentriccams. Each of the eccentric cams is rigidly connected to a gear whichmeshes with a further gear which is positioned rotatably and slidably inthe longitudinal direction on a shaft. This last mentioned gear has alongitudinal slot in its axial bore which upon a shifting of the gear inan axial direction can be brought into a gripping engagement with one oftwo wedges which is arranged on the drive shaft. This occurs only if thewedge, which is positioned in the direction in which the gear is moved,is located in alignment with the longitudinal slot. The wedges arearranged in two axial directions on the drive shaft, i.e., they aretransposed by The axial movement of the gear is effected by one of twoelectromagnets, and the return of the gear is accomplished by springs.

The advantage of the last mentioned arrangement for shifting the typecylinder is that the operation of the individual stages of the combinedplanetary gear mechanism is carried out directly through the eccentriccams. However, this advantage is considerably weakened by the fact thatthe control of the eccentric cams is costly, and, moreover, requireshigh shifting energy in order to move the gear in both directions.

Accordingly, it is a further object of the invention to provide animproved arrangement of eccentric cams for operating a combinedplanetary gear mechanism of a print setting apparatus.

Another problem of the prior art is the inadvertent errors andinaccuracies which occur in the manufacture of the eccentric cams. Insuch case, if the eccentricity is not precisely correct, the input tothe gear stages of the combined planetary gear mechanism is directlyaffected. Correction of the eccentricity of the eccentric cams can onlybe accomplished by very expensive adjustment, if the previously knownmethods are employed.

Accordingly, it is another object of the invention to provide animproved mechanism for adjusting the input to a combined planetary gearmechanism utilized in setting a type cylinder wherein the individualstages of the planetary gear mechanism are operated by eccentric camswhich are subject to variance in manufacture.

SUMMARY The invention relates to an apparatus for setting symhols whichare arranged circumferentially on a type cylinder in eight symbol rowsextending in an axial direction. The apparatus includes a combinedplanetary gear mechanism which, depending on the input thereto iseffective to position the type cylinder. The combined planetary gearmechanism includes a first sun gear which is driven in the first stageof the planetary gear mechanism and at the same time forms the drivinggear for the second stage of the combined planetary gear mechanism.

Since one of the two sun gears is mounted between the two stages of thecombined planetary gear mechanism, the mass to be moved during a cycleis decreased. This also results in the special advantage of being ableto mount the bushings for the planetary gears directly on thenon-rotating principle axis of the planetary gears.

In the instant combined planetary gear mechanism, the gear ratio of thefirst stage from the first sun gear over the planetary gear pair to thesecond sun gear is 3:1 2:3=2:l; and the gear ratio of the second stagefrom the aforementioned second sun gear to the power take-off sun gearover the intermediately positioned planetary gear pair is 2:l l:1:2:1.In this manner, the sun gear positioned between the two stages of thecombined planetary gear mechanism is utilized twice without the need forexcessively increasing the planetary gears to achieve the gear ratio of2:1 per gear stage.

According to a further improvement of the invention, the coupling systemincludes a plurality of eccentric cams which are positioned freelyrotatably on a driving shaft. The shaft is provided with a verticallyoriented, elongated slot for receiving a slidable wedge. The wedge iseffective to rotate the cam when the wedge is engaged in a complementarygroove provided interiorly and axially on the cam. On both sides of thewedge there are arranged resilient elements which influence the wedgeselectively in one of two directions, in one of which the wedge canenter the groove in the cam and in the other of which it cannot. Themovement of the wedge takes place during a short pause of the driveshaft, which is provided for by a three wheel eccentric mechanismconnected between the drive motor and the drive shaft. The abovedescribed arrangement has the advantage of reducing the energy whichmust be expended for coupling the cams. This was one of thedisadvantages of the shiftable gear arrangement which was known in theprior art, and is described hereinabove.

In a preferred arrangement of the coupling system according to theinvention, the resilient elements for setting the wedge are oppositelyacting spring elements arranged one on each side of the wedge for urgingthe wedge in either of two directions. The spring elements areintermittently spread apart by a two part cam which is mounted on thedrive shaft. While the spring elements are spread apart, a settingmechanism is actuated which selectively restrains one of the springelements and permits the other spring element to engage and move thewdege. It is also desirable that the wedge and the eccentric cam beprecisely positioned during the setting operation by a locating deviceof some sort to insure proper alignment.

In accordance with a further improvement of the invention, threeconnecting rods are provided, a first of which is mounted between afirst eccentric cam to a first sun gear, a second of which is mountedbetween a second eccentric cam and a first pair of planetary gears, andthe third of which is mounted between a third eccentric cam and a secondpair of planetary gears of the combined planetary gear mechanism. Theconnecting rods, which are driven by the eccentric cams, are attached byeccentrically positioned bolts to their respective sun gear andplanetary gear pairs so that they may be readily adjusted withoutrequiring the variance of the eccentricity of the cams themselves.

By simply turning the eccentrically positioned bolts, the angle of theconnecting rod to its respective connection in the combined planetarygear mechanism can be varied, thus, greatly reducing the manufacturingtolerances which are required of the eccentric cams.

DRAWINGS Other objects, other advantages and aspects of the inventionwill become apparent by reference to the following detailed descriptionand drawings of a specific embodiment thereof wherein:

FIG. 1 is a schematic view embodying the principles of the invention andshowing the driving apparatus of a type cylinder printer for use, forexample, in the telegraph art;

FIG. 2 is a front view of a two stage combined planetary gear mechanismfor driving a type cylinder, removed from the remainder of the apparatusshown in FIG. 1;

FIG. 3 is an exploded schematic view of the individual parts of a sleevebushing for supporting a planetary gear pair, and the associated forkedmember for connecting the bushing to its respective gear cage;

FIG. 4 shows a side elevational view taken along line 44 of FIG. 1, withportions removed, of an individual stage of the combined planetary gearmechanism with its respective coupling members;

FIG. 5 is an exploded schematic view of the mechanism shown in FIG. 4;and

FIG. 6 is an exploded schematic view of the eccentric attachment forsecuring a connecting rod to its respective gear cage.

DETAILED DESCRIPTION OF THE INVENTION The drive mechanism shown in FIG.1 serves to shift in an axial manner a type cylinder (not shown) of atelegarph apparatus, for example. The rotational shifting of the typecylinder can be carried out with another setting mechanism of the sametype. The output of the mechanism is indicated by the arrow A, andshould be connected through appropriate gears if axial movement, asopposed to rotative movement, is desired.

The drive of the entire setting apparatus is controlled by a shaft 1,(FIG. 1) labeled INPUT, which rotates with a constant speed in thedirection indicated by arrow B. The input shaft 1 is connected through athree gear eccentric mechanism 2 to a drive shaft 3. With a constant andequal rotational speed applied to the shaft 1, the three gear eccentricmechanism 2 causes the shaft 3 to rotate in the same direction as shaft1, as indicated by arrow. C. The rotational speed of shaft 3 changeseach cycle from zero to a maximum and then to zero again.

A trio of eccentric cams 4', 4" and 4" are rotatably positioned on theshaft 3. During the idle phase of the shaft 3, the cams 4', 4" and 4"may be coupled therewith for a half of a revolution depending on theposition of a trio of setting elements, 5', 5" and 5". In other words,the particular setting of the setting elements 5', 5" and 5" determineswhether or not their respective cams are coupled to the shaft 3 duringthe idle phase. The setting elements 5', 5" and 5" have a rocking motionapplied thereto by the magnets 44 to move the setting elements into oneof two positions. The three eccentric cams 4, 4" and 4' are effective todrive the individual stages of the combined planetary gear mechanismthrough their respective connecting rods 6, 6" and 6". The firsteccentric cam 4' acts through its associated connecting rod 6' on afirst sun gear 7 of the combined planetary gear mechanism. The secondeccentric cam 4" acts through its associated connecting rod 6" on a pairof planetary gears 8 and 9 which are positioned in a cage 14 and whichorbit around the first sun gear 72 and a second sun gear 12,respectively. The third eccentric cam 4" acts through its associatedconnecting rod 6" on a sec- 0nd pair of planetary gears and 11 which arepositioned in a cage and which orbit around the second sun gear 12 and athird sun gear 13, respectively. The actual driving of the type cylinder(not shown), which is connected to an output shaft 42, is effected bymeans of a gear 16 which meshes with the third sun gear 13 of thecombined planetary gear mechanism.

FIG. 2 shows the two stage combined planetary gear mechanism which iseffective through the third sun gear 13 and the gear 16 to position theoutput shaft of 42 to which is connected a type cylinder (not shown).The three sun gears 7, 12 and 13, as well as the two planetary gearcages 14 and 15, which position the two planetary gear pairs 8-9 and10-11, respectively, are mounted for free turning movement on a shaft17. The connecting rod 6' is connected through a link 18 to the firstsun gear 7. The connecting rod 6 is secured to the cage 14, and thethird connecting rod 6" is secured to the cage 15. The gear ratiofromthe first sun gear 7 to the planetary gear 8 is 3:1; and the gearratio from the planetary gear 9, which is rigidly connected to theplanetary gear 8, to the sun gear 12 is 2:3. Therefore, the gear ratiofrom the sun gear 7 to the sun gear 12 is 2:1. The gear ratio from thesun gear 12, which meshes with the planetary gear 9 as well as with theplanetary gear 10, to the planetary gear 10 is 2:1; and the gear ratiofrom the planetary gear 11 to the sun gear 13 is 1:1. Therefore, a totalgear ratio of 4:2:1 results.

The planetary gear pairs 8-9 and 1011 are positioned in sleeve bushings19-20 and 21-22 in cages 14 and 15, respectively. The bushings and 22are pressed firmly into the cages 14 and 15, respectively, while thebushings 19 and 21 are held by forked members 23 and 24, respectively,in the cages 14 and 15. The bushings 19 and 21 must be removable inorder to enable the insertion of the planetary gear pairs 8-9 and 1011into their respective cages 14 and 15.

FIG. 3 shows a portion of the cage 15 with the bushing 21 and the forkedmember 24. In the assembled condition, the forked member 24 extends intoa pair of notches 25 in the bushing 21; and the bore 26 of the forkedmember 24 is mounted on the shaft 17.

The setting movement of the letter-digit commutation rnav be controlledby a S-unit-code telegraph apparatus which is known in the art. If a6-unit-code is employed the letter-digit commutation is carried out bythe sixth code step.

The coupling apparatus which is required once for each setting cycle ofthe type cylinder is shown in FIG. 4 in a side elevational view. Thereis also shown in FIG. 4 the eccentric cam 4" with its associatedconnecting rod 6 which is secured to the cage 15. The cage 15 in turnorbits the planetary gear pair 10-11 depending on the input which isapplied via the connecting rod.

The arrangement of FIG. 4 is shown in FIG. 5 in an exploded view. Theshaft 3 is provided with an elongated slot 41, one for each of theathree eccentric cams and the associated connecting rods. A wedge 28 isslidably mounted in each of the slots 41. The length of the wedge 28(without the recessed portion) corresponds to the diameter of the shaft3. The eccentric cam 4 which is to be coupled to its associatedconnecting rod is loosely positioned on the shaft 3 and extends halfwayacross the slot 41 and the wedge 28. A coupling connection existsbetween the shaft 3 and the eccentric cam 4" if the wedge 28 extendsinto a complementary longitudinal groove 29 which is provided in theaxial bore of the eccentric cam 4". When the shaft 3 is in its idlecondition, a spring biased roller 30 extends into one of two notches 31arranged in opposite sides of each of the eccentric cams 4 therebyaccurately locating the cams in the idle position. A locating device 45can be used to position the wedge 28 in the idle position.

A two-part cam 32 is mounted on the shaft 3, there being one such cam 32for each of the eccentric earns 4', 4" and 4". The two-part cam 32 iscoupled to the shaft 3 by a groove 33 which receives the wedge 28mounted in the slot 41. By means of this two-part cam 32, the two legsof a V-shaped leaf spring 34 are spread apart on each operational cycleand are then released after each half-revolution of the shaft 3. In theoperational area of the ends of the leaf spring 34, there is positioneda crescent-shaped attachment 35 of the respective setting member 5". Thesetting members 5 are designed as the armature of a magnet and areshiftable by energization of magnets 44 against the influence of aspring (not shown). The upper and lower ends of the crescentshapedattachment 35 of the setting member 5 are effective to restrain theupper and the lower legs of the leaf spring 34, respectively, dependingon the position of the setting member. In FIG. 4 the setting member 5"is forward (to the right) and the upper end of the leaf spring 34 isrestrained; the lower end is effective to urge the wedge 28 upwards. Inthe rearward position (to the left) the lower end of the leaf spring 34is restrained and the upper end urges the wedge 28 downwardly. Theposition of the setting members 5 is determined by the signals which aresent to the magnets 44. The leg of the leaf spring 34 which is notrestrained is effective to act on the wedge 28 and shift the same, if ashifting into the desired direction is possible and if the wedge is notalready in the desired position through a prior setting. If, after thedesired shifting of the wedge 28, the wedge 28 extends into the groove29 of the eccentric cam 4 a coupling connection is established betweenthe drive shaft 3 and the eccentric cam 4 for one-half of a revolution.If the groove 29 of the eccentric cam 4 is not aligned with the shiftedwedge 28, then the wedge 28 only supports itself at the interior wall ofthe axial bore of the eccentric cam 4 and no coupling connection resultsbetween the shaft 3 and the eccentric cam 4.

The motion of the setting member 5 must occur when the two legs of theleaf spring 34 are spread apart. In the example described above, this isnot the case in the idle position, so that the motion of the settingmember 5 must occur prior to the reaching of the idle position. Thismeans that the evaluation of a symbol of a binary code extends over thetime period of about 1 /2 symbol length. As long as a plurality ofsymbols is evaluated in quick succession, this is of no disadvantage. Insuch a case, the motion of the setting members 5 can take place duringthe evaluation of the preceding symbol. As a rule, only individualsymbols, or individual small groups of symbols, are evaluated, and theapparatus is stopped by a special circuit coupling during the pauses. Insuch a case, it is advantageous to supplement the above describedcoupling system with an additional mechanism.

As is shown in FIG. 5, this supplemental mechanism consists of a disc 36which is rotatably positioned on the shaft 3 in the area of the cam 32.The disc 36 is provided with two extensions 37 and an actuation lever38. In the idle position, the extensions 37 of the disc 36 are turned insuch a manner that the ends of the leaf spring 34, which are spreadapart by the two-part cam disc 32, support themselves on the extensions37. Thus, the motion of the setting member 5 can take place in thisposition. Shortly before the rotation of the shaft 3, the disc 36 isrotated by the actuation lever 38 so that the extensions 37 release theends of the leaf spring 34 and the desired movement of the wedge 28 cantake place.

A coupling connection results in the above described coupling systemonly when the next following setting criteria deviates from thepreceding setting criteria. This is so since the groove 29 in theeccentric cam 4 is located in a position, after the advancement of theshaft 3 according to one criterion, which is different from the settingposition caused by a similar setting criterion. Thus a couplingconnection can no longer take place.

FIG. 6 shows a portion of the cage 15 and additionally discloses anattachment screw 39 which fits in a bore 27 in the planetary gear cage15. The screw 39 is threaded into an eccentric bore of a bolt 40 foraifixing the connecting rod 6 to the cage 15. By turning the bolt 40 onthe threaded screw 39, the setting angle between the connecting rod andthe cage 15 can be changed. The connection of a similar eccentricallybored bolt to the link 18 of the first sun gear and another to theplanteary gear cage 14 permits similar adjustment of the otherconnecting rods.

It has been found that an eccentric positioning of the bolts 40 by 0.15mm. at a turning radius at about 12 mm. and a normal shifting angle of45 results in a change of this shifting angle by over 1.

The above described coupling system according to the invention is Verysimple in its construction and mode of operation. Moreover, a very lowcontrol power is necessary to operate the coupling system. In addition,only two control positions are required.

Preferably, a two-legged leaf spring 34 is employed for each couplingunit to shift its associated wedge. The operational ends of the leafsprings, which are either acting on the wedge 28 or are restrained bythe crescent shaped member 35 of the setting member 5, are directed inthe same direction of rotation in relation to the drive axis,preferably, in the direction of rotation of the drive shaft. This isadvantageous since the setting paths of the setting elements can therebybe kept to a minimum.

The above described improved coupling system according to the inventionis advantageous if a plurality of symbols are to be printed in quicksuccession, since the setting criteria for the printing of a symbol mustbe rendered effective no later than after one-half of the previousoperational cycle. This takes place during the printing of the previoussymbol, and thus no loss of time occurs.

If only individual symbols or symbol groups are usually printed, then itis advantageous to employ between the motor (not shown) and the threegear eccentric mechanism 2, or even instead of the three gear eccentricmechanism 2, an ordinary electromagnetically controlled circuit coupler.Such a coupler would hold the drive shaft of the couplings for one-halfof a revolution per symbol, thus stopping the apparatus in theoperational phases. However, it is then desirable to utilize asupplemental system, described above as disc 36, which is characterizedby the fact that it has extensions 37 which act as supporting membersfor the spring elements 34 in the idle position of the shaft. After thecompleted setting of the setting elements and prior to the beginning ofhe rotary movement of the drive shaft 3, the leaf spring 34 is releasedby turning the disc 36 and its associated extensions 37. The rotation ofthe actuation levers can suitably be accomplished by the use of magnets.

In addition to the above-described utilization of the instant apparatus,the eccentric cam of the coupling system according to the invention canfor example, also be employed for lifting, lowering and advancing a typecylinder and for the line advancement.

What is claimed:

1. An apparatus for setting symbols which are arranged on thecircumference of a type cylinder in eight axial rows, which comprises:

a two stage combined planetary gear mechanism for driving the typecylinder, which includes:

first (7), second (12) and third (13) sun gears;

a first pair of integrally associated planetary gears (8, 9), one ofwhich (8) is in mesh with the first sun gear (7) and the second (9) ofwhich is in mesh with the second sun gear (12);

a second pair of integrally associated planetary gears (10, 11), one ofwhich is in mesh with the second sun gear (12) and the other of which(11) is in mesh with the third sun gear (13) so that the driven sun gear(12) of the first stage of the combined planetary gear mechanism formsthe drive for the sun gear (13) of the second stage of the mechanism,said gear stages having a gear ratio of 1 :2 or 2:1 per gear stage;

first (6), second (6") and third (6"') input connecting members, saidfirst input member (6) being directly connected with the first sun gear(7 and the second and third input connecting members being connected tothe first pair of planetary gears (8, '9) and the second pair ofplanetary gears (10, 11), respectively, for selectively supplying inputrotation to the gears of the combined planetary gear mechanism; and

means (4, 4", 4, etc.) for selectively actuating the connecting members(6', 6", 6") to vary the output of the combined planetary gear mechanismand properly position the type cylinder for the printing of the nextsymbol.

2. Apparatus as recited in claim 1 wherein the gear ratios in the firstgear stage including the first sun wheel (7 the first planetary gearpair (8, 9), and the second sun gear (12) are 3:1 2:3=2:1, and the gearratios in the second gear stage including the second sun gear (12), thesecond planetary gear pair (10, 11) and the third sun gear (13) are 2:l1:1=2:1.

3. Apparatus as recited in claim 1 which further includes:

sleeve bushings (19, 20 and 21, 22) for supporting the planetary gearpairs (8, 9 and 10, 11) in their respective cages; and

forked members (24) for engaging the bushings and releasably attachingone end of each of the planetary gear pairs to its respective cage.

4. Apparatus as recited in claim 1 wherein said actuating meanscomprises:

a drive shaft (3) having a longitudinally extending slot (41) which isperpendicular to the axis of rotation of the shaft;

means (1, 2') for applying intermittent rotation to the shaft (3),

a coupling apparatus for selectively conveying the intermittent rotativemotion from the shaft (3), to the connecting members which includes:

a cam (4) mounted freely on the shaft (3) for selectively receivingrotative motion therefrom, said cam having a longitudinal groove (29) inthe axial bore thereof, and said cam being effective to convey motion tothe connecting members;

a wedge (28) slidably positioned in the slot (41), said wedge beingreceivable in the longitudinal groove (29); and

means for shifting said wedge (28) in the slot (41) into one of twopositions, wherein in one of the positions the wedge (28) is in thegroove (29) and communicates. the rotation of the drive shaft '(3) tothe cam (4) and in the other position the wedge (28) is not in thegroove (29) and the cam (4) is disengaged from the drive shaft (3).

5. Apparatus as recited in claim 4 wherein said shifting means includes:

a pair of spaced spring elements (34), one positioned on either side ofthe wedge (28), said spring elements acting in opposite directions onthe wedge for urging the wedge in either one of the two positions;

a cam (32) mounted on the drive shaft (3) for cyclically spreading thespring elements (34) away from the wedge (28);

setting means (5), operable while the spring elements are spread awayfrom the wedge, for selectively positioning the wedge, said settingmeans having two operating positions, in one of which a first of thespring elements is restrained while the second spring element acts onthe wedge, and in the other operating position the second spring elementis restrained while the first spring element acts on the wedge.

6. Apparatus as recited in claim which further comprises:

an actuation lever (38) having two extensions (37) for supporting thespring elements (34) in the spread apart position while the. drive shaft(3) is in the idle condition, said lever being rotatable after theactuation of the setting member (5) and prior to the next rotation ofthe drive shaft (3) to release the spring elements (34).

7. In combination with an apparatus for setting symbols which arearranged on a type cylinder, said cylinder being drivable by a combinedplanetary gear mechanism having inputs from a plurality of cams, theimprovement which comprises:

a drive shaft (3) having a longitudinally extending slot (41) which isperpendicular to the axis of rotation of the shaft;

means (1, 2) for applying intermittent rotation to the shaft (3),

a coupling apparatus for selectively conveying the intermittent rotativemotion from the shaft (3), to the connecting members which includes:

a cam (4) mounted freely on the shaft (3) for selectively receivingrotative motion therefrom, said cam having a longitudinal groove (29) inthe axial bore thereof, and said cam being effective to convey motion tothe connecting members;

a wedge (28) slidably positioned in the slot (41),

said wedge being receivable in the longitudinal groove (29); and

means for shifting said wedge (28) in the slot (41) into one of twopositions, wherein in one of the positions the wedges (28) is in thegroove (29) and communicates the rotation of the drive shaft (3) to thecam (4) and in the other position the wedge (28) is not in the groove(29) and the cam (4) is disengaged from the drive shaft (3).

8. Apparatus as recited in claim 7 wherein said shifting means includes:

a pair of spaced spring elements (34), one positioned on either side ofthe wedge (28), said spring elements acting in opposite directions onthe wedge for urging the wedge in either one of the two positions;

a cam (32) mounted on the drive shaft (3) for cyclically spreading thespring elements (34) away from the Wedge (28);

setting means (5), Operable while the spring elements are spread awayfrom the wedge, for selectively positioning the wedge, said settingmeans having two operating positions, in one of which a first of thespring elements is restrained while the second spring element acts onthe wedge, and in the other operating position the second spring elementis restrained while the first spring element acts on the wedge.

9. Apparatus as recited in claim 8 which further comprises:

an actuation lever (38) having two extensions '(37) for supporting thespring elements (34) in the spread apart position while the drive shaft(3) is in the idle condition, said lever being rotatable after theactuation of the setting member (5) and prior to the next rotation ofthe drive shaft (3) to release the spring elements (34).

10. Apparatus as recited in claim 8 which further comprises apositioning device (45) for locating the wedge (28) after each cycle.

11. Apparatus as recited in claim 8 wherein said cam (4) has a pair ofopposed notches (31) in the periphery thereof; and which furtherincludes:

a spring biased roller (30) receivable alternately in the notches forpositioning the cam after each cycle (one half revolution).

12. Apparatus as recited in claim 7 wherein said cam (4) is connected tosaid combined planetary gear mechanism by a rod (6) which communicatesthe rotative motion of the cam to the combined planetary gear mechanism,and which further comprises:

an eccentrically and interiorly thread bolt (40) on which is mounted theoutput end of the. rod (6); and

and exteriorly threaded screw (39) for connecting the bolt (40) to thecombined planetary gear mechamsm,

whereby the angle of the rod (6) can be varied with respect to thecombined planetary gear mechanism by turning the bolt (40).

13. In combination with a S-unit code telegraph apparatus for settingsymbols which are arranged on the circumference of a type cylinder ineight axial rows, under the control of a successively switched two stagecombined planetary gear path mechanism having a gear ratio of 1:2 or 2:1per stage and settable by actuating means through binary codecombination steps corresponding to the code-combination digit or letterchange, the sun gear of the first stage and the. two planetary gearpairs of the two stages being actuable by connecting rods into twopositions each, wherein the improvement comprises:

said driven sun gear of the first stage of the combined planetary gearpath mechanism forms the driving sun gear of the second stage of thecombined planetary gear path mechanism.

JOHN W. CALDWELL, Primary Examiner M. M. CURTIS, Assistant Examiner US.Cl. X.R.

